CN101896732B - Shock absorber with increasing damping force - Google Patents
Shock absorber with increasing damping force Download PDFInfo
- Publication number
- CN101896732B CN101896732B CN2008801209286A CN200880120928A CN101896732B CN 101896732 B CN101896732 B CN 101896732B CN 2008801209286 A CN2008801209286 A CN 2008801209286A CN 200880120928 A CN200880120928 A CN 200880120928A CN 101896732 B CN101896732 B CN 101896732B
- Authority
- CN
- China
- Prior art keywords
- piston
- damping
- damping piston
- vibration damper
- damper according
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 238000013016 damping Methods 0.000 title claims abstract description 347
- 239000006096 absorbing agent Substances 0.000 title abstract description 6
- 230000035939 shock Effects 0.000 title abstract description 6
- 238000006243 chemical reaction Methods 0.000 claims description 23
- 230000008859 change Effects 0.000 claims description 9
- 230000009467 reduction Effects 0.000 claims description 2
- 230000006835 compression Effects 0.000 description 7
- 238000007906 compression Methods 0.000 description 7
- 238000012856 packing Methods 0.000 description 7
- 230000001133 acceleration Effects 0.000 description 5
- 238000000034 method Methods 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 230000000750 progressive effect Effects 0.000 description 4
- 230000001105 regulatory effect Effects 0.000 description 4
- LYCAIKOWRPUZTN-UHFFFAOYSA-N Ethylene glycol Chemical compound OCCO LYCAIKOWRPUZTN-UHFFFAOYSA-N 0.000 description 3
- 239000000654 additive Substances 0.000 description 3
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 2
- 230000000996 additive effect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 239000007789 gas Substances 0.000 description 2
- 239000010720 hydraulic oil Substances 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 239000003989 dielectric material Substances 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000011521 glass Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 229910052757 nitrogen Inorganic materials 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- LENZDBCJOHFCAS-UHFFFAOYSA-N tris Chemical compound OCC(N)(CO)CO LENZDBCJOHFCAS-UHFFFAOYSA-N 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
- 230000037303 wrinkles Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/48—Arrangements for providing different damping effects at different parts of the stroke
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
- F16F9/516—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics resulting in the damping effects during contraction being different from the damping effects during extension, i.e. responsive to the direction of movement
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
- F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
- F16F9/3481—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body characterised by shape or construction of throttling passages in piston
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
- F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
- F16F9/3485—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body characterised by features of supporting elements intended to guide or limit the movement of the annular discs
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/48—Arrangements for providing different damping effects at different parts of the stroke
- F16F9/49—Stops limiting fluid passage, e.g. hydraulic stops or elastomeric elements inside the cylinder which contribute to changes in fluid damping
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Fluid-Damping Devices (AREA)
Abstract
The invention relates to an arrangement in a vehicle shock absorber (1) for generating an additional counter-force (F2) acting counter to the direction of movement in the limit position (s) (R1) of a movement /stroke between the parts (4, 2) of the shock absorber moving relative to one another, and to a shock absorber (1) comprising such an arrangement. The shock absorber in both cases substantially comprises a damping medium-filled damping cylinder (2), divided into two damping chambers (Cl, C2), by a main piston (5), axially moveable relative to the damping cylinder (2) and attached to a piston rod (4). Also arranged around the piston rod (4) is a second piston/damping piston (5), which contains one or more first and second through-ducts (9, 10), which are defined by first and second flow-limiting devices (11, 12), preferably consisting of multiple thin first washers. The damping piston (5) is intended to slide in a restricting space (6) located in the damping cylinder (2), and having an inside diameter smaller than the inside diameter of the damping cylinder. The additional counter- force counter (F2) is substantially constant throughout the entire stroke in order to create gentle braking of the damping movement.
Description
Technical field
The present invention relates to a kind of traffic tool vibration damper (vehicle shock absorber), this traffic tool vibration damper comprises substantially: the damped cylinder (damping medium-filleddamping cylinder) that is filled with resisting medium, it is divided into two damped cylinders, namely is connected to compression cylinder (compression chamber) and the reversion cylinder (return chamber) of piston rod by main piston.Main piston moves and moves axially with compression and reversion in damped cylinder.When vibration damper reaches a certain compressive state, move through the effect braking that increases damping.
Background of invention
The vibration damper of this type is disclosed by for example EP0565832, GB998742 or the applicant's patent EP1006292B1, wherein, compression is mobile by the second piston deceleration, and referred to here as damping piston, it reaches the cup that has less than the diameter of damped cylinder in a certain length of stroke.
In the vibration damper of the progressive damping with this type, verified: the gentleness braking (gentle braking) that produces the damping movement in the restriction site (limit position) is a problem.When the second piston reached the cup of small diameter, piston had high speed, and it produces large braking force on every side at maximum bonding point.Then reaction force reduces along with reducing of speed.
Vibration damper according to EP1006292 structure for example has the second piston, and this second piston has a plurality of thin packing rings, i.e. so-called shim packs (shim stack), and it is opened under a certain power effect.When the pressure-acting in the cup produces breaking force during in the opened areas of shim packs.By regulating the corresponding layout of size, thickness, number and packing ring (pad), can change the opening characteristic of shim packs.The relatively the most normal generation of progressive damping characteristic, it provides the power that increases along with speed, and when the second piston engaged to enter at a high speed, this speed caused power to produce large increase at time per unit.This behavior may be a problem for the driver of the traffic tool, because then braking may be perceived as jerking movement (jerky).The risk of the quick change in the distribution that causes the support between road surface and the different wheel is being emitted in the quick change of the power between wheel and the road surface.This is so that the operation of the traffic tool is more difficult, because its predictability variation.Therefore, it is the obstruction damping force of constant as far as possible that expectation has in mobile whole braking process, has the reaction force that increases along with the speed that increases with replacement.
EP0565832 has also illustrated the 3rd problem of known technology, also namely produce the problem of function, this function will not need the second piston to contribute simultaneously to how much to cross constrained systems and abundant controllable braking to damping movement is provided, its locking or require split-hair tolerance of may becoming.In EP0565832, have significantly outer diameter less than the inner diameter of cup with the second piston, and solve this problem by the mode that flexible gaskets absorbs any movement radially.EP1006292 has also solved this problem in the mode that the second piston has less than the outer diameter of the inner diameter of cup.Yet in this case, the seepage stream of the resisting medium in the outside of process piston is deducted from total braking action, and, braking characteristic is not to be determined separately by the opening characteristic of shim packs yet.At low velocity of piston place, braking characteristic is determined separately by the magnitude of seepage stream in principle.In these two cases, this has caused very progressive damping characteristic, also be damping force along with speed sharply increases, have the shortcoming of all above-mentioned hints.
Goal of the invention
The invention is intended to solve the problem that produces mobile gentleness braking in the restriction site that vibration damper moves, it will stop the tactile end (bottoming) in the dampening arrangement, and gentle braking produces the precondition of the predictable comfortable traffic tool of driver.
The present invention has also solved and has guaranteed for the power of braking damping movement along with the obvious problem that increases of speed.
The present invention has also solved further problem, does not namely need the second piston to contribute to what can lock and how much crosses constrained systems and allow abundant controllable braking to damping movement.
In addition, do not need the invention is intended to the plain mode of utmost point precision tolerance to solve these problems.
Summary of the invention
The present invention relates to the layout in the traffic tool vibration damper, this is arranged for generation of additional reaction force, this reaction force reacts on the movement direction in the restriction site of the movement/stroke between the parts of relative to each other mobile vibration damper, and the invention still further relates to the vibration damper that comprises this layout.
In both cases, vibration damper comprises the damped cylinder that is filled with resisting medium of hydraulic pressure basically, and this damped cylinder is divided into two dampening chamber, for example pressing chamber and reversion chamber.Two dampening chamber are separated by main piston, and this main piston is axially removable and be connected in the damping piston holder with respect to damped cylinder, and this damping piston holder is fixed in the part of piston rod or forms the part of piston rod.Also in the piston rod arranged around at least the second piston/damping piston, the first side of this second piston/damping piston is to main piston, and comprises one or more the first siphunculus (through-duct) and the second siphunculus.These pipes are defined with flow direction by flow limiter, and this flow limiter produces the restriction of resisting medium stream, and this flow limiter preferably shows as one or more thin the first packing ring or pads.The first pipe in these pipes is limited by the first flow limiter in the first side of damping piston.Damping piston has the piston outer diameter less than the outer diameter of main piston, and be used for be arranged in and hydraulic link in the slip of the restricted quarter (restricting space) of damped cylinder.The restricted quarter of form that can present cup for example has the inner diameter less than the inner diameter of damped cylinder.
The damping movement braking begins in a certain length of stroke that arrives the distance of the restricted quarter corresponding to damping piston.The reaction force that reacts on movement direction of vibration damper is partly from the pressure drop on the main piston, the partly pressure drop on the damping piston when engaging in the restricted quarter when damping piston.When damping piston when its restriction site moves and is arranged in the parts of the restricted quarter that generation engages fully, the power of damping piston is in fact constant in the whole stroke to a great extent.This is the design owing to damping piston, and this design produces as the very little damping force of the change of velocity function.This be implemented be because: the resisting medium stream that acts on the first flow limiter is designed to work in a space, and this space is between the side away from movement direction of first-class moving restricting means and damping piston.This space has large outer diameter scope, when opening flow path by the first pipe with the pressure reduction on the convenient damping piston, the restriction of resisting medium stream is along with the mobile minimum level ground that increases changes, also be, even in relatively large situation about flowing, it still produces the lower raising height (lifting height) of the first flow limiter.The little variation of the pressure drop when this causes flowing variation on the first flow limiter.
Subsequently, when opening by the flow path of the first pipe, the first flow limiter rises a certain raising highly from damping piston, in order to produce opened areas between the side away from movement direction of the first flow limiter and damping piston.This opened areas is determined the restriction of resisting medium stream.
Being minimized through the seepage of piston stream, also is that the function that flows as pressure between the internal surface of damping piston and the restricted quarter changes less.Damping piston is designed to respect to the piston retainer to move axially, so that minimum seepage stream becomes possibility.Then big difference that need to be between the internal surface of the outer diameter of damping piston and the restricted quarter just may be realized the modulation of the restricted quarter.
In order to allow a certain of independent piston to move radially, and, deficiently with axial locking.This means that the tension that changes as the function with respect to the position of the damping piston of the device that keeps damping piston is subjected to axially movable the impact.Tension is possible by the geometry designs of the first flow limiter.Flow limiter remains between the out-damping piston face and internally-damped piston face that relative to each other axially departs from.When flow limiter is in maximum tension, require to be used for opening the maximum reaction force of the first flow limiter.When damping piston reaches it when maximum towards moving axially of main piston, obtain maximum tension.Then flow limiter presses to (bear against) internally-damped piston face and out-damping piston face.The speed of piston rod is lower, and is lower by the collision stream of damping piston, so the pressure drop on the damping piston is lower, also is that damping piston is reduced towards moving axially of main piston.
Have for pressure and work so that producing the design on the large surface of tension means, even in the little situation of the pressure drop on the damping piston, also namely strain in the situation of the corresponding low-down speed of constant that keeps low, can reach tension.Because to reach when engaging into the cup-shaped restricted quarter fully speed usually maximum when damping piston, tension and also reached maximum at this point by flowing of the first flow limiter, the power that also namely acts on the first flow limiter is maximum.Because the design of flow limiter is contributed to damping piston, when flow increasing, this damping piston so that pressure drop slightly increase, reaction force even along with speed keeps reliably, therefore flowing also diminishes.When damping piston reached its restriction site, speed descended, and reaction force also diminishes.
In another mode of execution of arranging, in the restriction site of two stroke direction, produce additional reaction force, because damping piston is arranged in each dampening chamber.Two damping pistons all are oriented to their the first side to main piston.
This design means that damping piston is removable at axial direction and radial direction with respect to piston rod.Thereby do not need damping piston to catch or do not need a large amount of play (paly) between the inner diameter of damping piston and the restricted quarter, just may realize the modulation in space processed.
Vibration damper is characterised in that, the first damping piston siphunculus leads in the inner diameter scope and the space between the outer diameter scope between damping piston the first side and the first movement restriction device.The space has greater than the siphunculus/zone of the first siphunculus or the constricted zone of overall area.The space also has a certain degree of depth, so that resisting medium can move therein.Damping piston comprises at least two the first siphunculus and with at least two spaces that the first siphunculus links together.Even when flow limiter was brought up to little raising height from damping piston, the outer diameter scope in space produced large opened areas.This means that when the first flow limiter was opened, damping force only changed slightly with in response to the change in flowing.
Damping piston also is designed to have the radial internal clearance around the damping piston holder, but has the minimum play between the inner diameter of damping piston and the restricted quarter.Thereby damping piston can be radially mobile with respect to the damping piston holder.Damping piston can also be axially mobile with respect to the damping piston holder, this move through be arranged in the damping piston holder or on two position limitation spares restrictions.
In the first mode of execution of the present invention, damping piston moves with to resistive drag force at axial direction.This resistance produces by the elastic device that is arranged between damping piston and the position limitation spare.
In another mode of execution, damping piston moves to resist the resistance that produces in the tension by the first flow limiter.The generation of this tension is owing to following reason: during the first flow limiter is designed to be in the close position, to press to the first damping piston surface and the second damping piston surface of relative to each other departing from.The first damping piston surface is arranged on the first side of the damping piston in the inner diameter scope in space, and the second damping piston is arranged in outside the outer diameter scope in space.Damping piston also can naturally be arranged in case it move to resist from elastic device and tightening force in conjunction with resistance.
In the 3rd mode of execution of vibration damper, two damping pistons are arranged on the piston rod, first side at main piston, and another is in the second side of main piston.Two damping pistons have their the first side towards main piston.
Describe the present invention in detail hereinafter with reference to accompanying drawing.
Description of drawings
Fig. 1 represents according to vibration damper of the present invention.
Fig. 2 a represents according to the present invention and according to the power-velocity chart of the main piston of prior art.
Fig. 2 b represents according to the present invention and according to the power-velocity chart of the damping piston of prior art.
Fig. 2 c represents according to the present invention and according to the main piston of the damping piston with interpolation of prior art, also is the power-velocity chart of whole vibration damper.
Fig. 2 d represent according to the present invention and the vibration damper according to prior art in the acceleration chart in time that absorbs.
Fig. 3 a represents the enlarged view according to the second piston of the present invention/damping piston.
Fig. 3 b represents to have first flow limiter of closing and does not have the further enlarged view of the damping piston of tensioning.
Fig. 3 b represents to have the further enlarged view of the first flow limiter of opening and the damping piston with tensioning.
Fig. 4 a-4c represents to have the damping piston of size.
Detailed Description Of The Invention
Fig. 1 represents according to vibration damper 1 of the present invention.Vibration damper 1 in the present embodiment comprises damped cylinder 2, and the main piston 3 that this damped cylinder 2 is filled with resisting medium M1 and is connected to piston rod 4 is divided into two dampening chamber.Resisting medium M1 is preferably hydraulic oil, and it can comprise the associated additives of type known in the art.Alternatively, ethylene glycol and/or water can be used as fluid.Two dampening chamber can be called pressing chamber C1 and reversion chamber C2 because main piston 3 is axially mobile with compression direction in damped cylinder 2, and reversion move with traffic tool wheel and chassis with direction R1, R2 towards or deviate from each other the ratio that is moved into.Has outer diameter d
5ySecond piston or 5 of damping pistons on damping piston holder 13, this damping piston holder 13 is positioned at the upper piston rod end 4a place on the compressed side of main piston 3.Damping piston 5 is designed in the restricted quarter 6 axially mobile, and this restricted quarter 6 is limited by cup shell 6a in fact.The restricted quarter 6 has inner diameter d
6i, this inner diameter d
6iInner diameter d less than damped cylinder 2
2iLower piston rod end 4b has the first fixing device I 1, end eye for example, and it prepares for damper is connected to the part of the traffic tool, under discussion along with move on the road surface that is preferably below wheel or the runner.At 2a place, the upper end of damped cylinder 2, damper comprises the second fixing device I 2, and such as the cylinder head of the related top of tool eye, it can be connected to chassis or the frame part of the traffic tool under discussion.Naturally also the direction of assembly may be put upside down.
In example embodiment, vibration damper is the pressurized damper, wherein, resisting medium in the damped cylinder is pressurized via pressing chamber by pressurized reservoir 7, this pressurized reservoir 7 outwards or upcountry is positioned at the damped cylinder inboard, and these pressurized reservoir 7 disposed inboard have the pressing means 7a of the form that is piston, rubber bubble or analog.Pressurized reservoir in the first space 7b is surrounded the resisting medium that is preferably the aforementioned hydraulic oil (on seeing) with additive or other fluids.Pressurized reservoir is also limited by pressing means 7a in second space 7c, and this second space 7c comprises than the more compressible second medium of damping medium.Compressible medium can be made of gas, such as for example air, nitrogen or have other gases of additive.Produce the basic pressure of compression damping medium with compressible Filled Dielectrics second space.Compressible medium also available mechanical component such as spring or analog replaces.
The pressurization of damper and the damping characteristic of damper are regulated by the one or more valves 8 according to prior art that are arranged between pressurized reservoir and the damped cylinder.
When damper was worked, piston rod 4 moved with respect to damped cylinder 2 with a certain speed, and a certain speed provides by main piston 3, and also flowed by a certain resisting medium of damping piston 5 at restriction site.In the damping stroke, when main piston 3 was positioned at axially near damped cylinder 2 middle, main piston 3 had the highest speed usually.When main piston begins near its restriction site, reach reverse position zero before speed reduce, and when piston rod reverses its movement direction, again increase.As long as the second piston/damping piston 5 is freely in dampening chamber, only main piston 3 contributes to the damping characteristic of damper.When piston rod 4 and damping piston 5 with direction R1 when restriction site moves and arrives glass 6a, see Fig. 1 a, it begins with the amount that is enclosed in the resisting medium in the restricted quarter 6 hostile.Then produced the additional force F2 that hinders mobile R1, this additional force F2 is added on the damping force F 1, and this damping force F 1 is produced by main piston 3 and this movement of damping force F 1 braking in restriction site and tactile end of obstruction damper.Pressure difference on effective constricted zone that the magnitude of reaction force F2 is worked by damping piston 5 and pressure is determined.Resisting medium stream is determined by the design of the pressure difference on the piston and restriction.
See Fig. 2 a-2c, its represent respectively main piston (Fig. 2 a), damping piston (Fig. 2 b) and have the power-velocity chart of the main piston (Fig. 2 c) of the damping piston of interpolation.Fig. 2 d represents the acceleration chart in time that absorbs in the vibration damper.
Fig. 2 a represents the example of the increase of the power that the pressure difference on the main piston 3 of vibration damper produces.The appearance of curve can considerably change, but always along with speed increases.When additional damping piston 5 in speed v
2Enter when engaging, speed can be said to be from v
0To v
2Change.
In Fig. 2 b, dotted line represents the example according to the built-in pressure of the damping piston 5 of prior art, and wherein, power is along with speed v increases significantly.The progressive increase of power is from relatively large seepage stream, and this relatively large seepage stream is through defining between the damping piston and damping cup of the restricted quarter in the prior art.Solid line represents the built-in pressure according to damping piston 5 of the present invention, and wherein power keeps substantial constant along with the speed increase.Illustrate, because must allow minimum seepage to flow through between overdamping piston and the damping cup herein even with the minor variations that power increases.
Fig. 2 c represents to have the power that the main piston of the damping piston of interpolation absorbs, and also is the absorption of the power of whole vibration damper.The solid line representative is according to vibration damper of the present invention, and dotted line is the vibration damper of prior art.In this case, suppose, when damping piston is bonded in the damping cup, damper be compressed in speed v
2The place occurs.This means that when using according to force-limiting device of the present invention, power is from F1
2Be increased to F1
2+ F2
2Simultaneously, the further continuous decrease velocity range of reaction force, and the damping capacity that absorbs (it is corresponding to the zone of chart below) can increase, and in the jerking movement without any increase.In the design structure according to prior art, when damping piston entered joint, damping force was from F1
2Be increased to F1
2+ F3
2Damping force F 1
2+ F3
2Greater than F1
2+ F2
2, but in lower speed v
1The place, in conjunction with damping force F 1
1+ F3
1Less than the F1 according to design structure of the present invention
1+ F2
1Therefore, the damping capacity of the combination that can absorb according to the design structure of prior art is less than design structure according to the present invention, and thereby vibration damper touch the end, the risk that also namely reaches maximum stroke length is larger.
Fig. 2 d represents to have the vibration damper (dotted line) of additional force-limiting device according to prior art and has the additional vibration damper according to force-limiting device of the present invention (solid line) and how produces and postpone along with the time.The orientated at steep inclinations of this curve also is that the driver experiences from damper energetically corresponding to heavy jerking movement.At time t
2The place, additional damping piston 5 meets with the restricted quarter 6, and speed is braked tempestuously with acceleration, and the value of this acceleration is a in the prior art
2, and this acceleration is a according to the present invention
1As shown, a
1Much smaller than a
2, its hint is braked movement with softer movement.
When piston rod is worked from restriction site with direction R2, see Fig. 1 b, only produce generally low pressure loss on the damping piston 5, and only produce the insignificant additional force that reacts on movement direction.Power is produced by the second flow limiter 12, and this second flow limiter 12 is used as check valve and opens in the situation of the small pressure difference on the damping piston.Damping characteristic with this direction R2 is mainly determined by the pressure drop that produces on the main piston 3.
Fig. 3 a represents the enlarged view of the second piston/damping piston 5.Damping piston 5 has the first flow limiter 11 and 12 restrictions of the second flow limiter that the first siphunculus 9 and the second siphunculus 10, the first siphunculus 9 and the second siphunculus 10 streamwises are one or more thin packing ring forms.The 3rd pipe (not shown) also can be arranged to move by piston, and this piston has fixing restriction, and the magnitude that flows by this restriction does not change as the function of pressure in fact.The number of pipe is by the total volume restriction of damping piston, because a certain quantity of piston material must be held to keep stability and the intensity of damping piston, but the total number of pipe is preferably 6-12.In pipe, the first pipe 9 in stroke guiding with towards the flowing of the direction of restriction site (compression), and the second pipe 10 in stroke guiding to deviate from the mobile of restriction site (reversion) direction.The first flow limiter 11 is positioned on the first side 5a of damping piston 5, therefore is intended to limit resisting medium flowing from the restricted quarter 6 to the common C1/C2 of dampening chamber.The second flow limiter 12 is positioned on the second side 5b of damping piston 5, and when damping piston 5 by band to the restricted quarter 6, when also being direction R1, the flowing of restricted passage the second pipe 10.When damping piston 5 to deviate from the direction of restriction site, when also namely moving with direction R2, the second flow limiter 12 is opened very slightly.Under the situation with the stroke of the direction that deviates from restriction site, insignificant reaction force is produced subsequently, but with in the situation of the stroke of the direction of restriction site, has stoped by opening of the second pipe 10 mobile.Open slightly for the second flow limiter 12, it is implemented as very thin packing ring, and it is crooked and allow the resisting medium process slightly.It also has at least three strong point 12a, 12b, 12c, with the direction towards restriction site, also is direction R1 when moving with convenient damping piston, reduces the bending of packing ring.
Damping piston holder 13 has a certain the first diameter d
13Damping piston holder 13 also can be said to be and comprise piston rod 4, if piston rod 4 is designed to for example exert pressure with the main piston flow limiter with screw thread space cover (threadedspacing sleeve), piston rod 4 replaces damping piston holder 13.Thereby the top 4a of piston rod 4 can be said to be and has the first diameter d
13=d
4a
The diameter d of damping piston holder 13
13Inner diameter d less than damping piston 5
5i, in order between damping piston 5 and damping piston holder 13, cause radial internal clearance x.Damping piston 5 can move in radial direction with respect to damping piston holder 13.
The position of damping piston 5 on damping piston retainer 13 determined by two the piston limiting components 14,15 that are arranged in the damping piston holder 13.In the mode of execution according to Fig. 2 a, the first piston limiting component is that locking ring 14, the second piston limiting components that are arranged in first piston rod end 4a place are the backstop take heel 15 as form that is produced by the variation in the zone of damping piston holder 13.Distance y between locking ring 14 and the heel 15
1The total height h that is a bit larger tham piston 5
Always, comprise flow limiter 9,10 height, so that piston can be with respect to piston rod to displacement distance y
2The distance y 2 of selecting preferably very short but on request so that damping piston can be freely to move radially.Mobile y
2Axial angle also can be regulated by stop washer 16a, 16b, this stop washer 16a, 16b have been placed between locking ring 14 and heel 15 and the flow limiter 9,10, it presses to the first side 5a and the second side 5b of piston.Moving axially of piston can be regulated by elastic device 18, and this elastic device 18 preferably is the form of packing ring or the flexible O shape ring of contracting wrinkle, and is arranged between damping piston 5 and the position limitation spare 14,15.
Fig. 3 b and Fig. 4 a-4c represent the enlarged view of damping piston, and wherein, the first damping piston siphunculus 9 leads to space 17, the inner diameter d of this space 17 between the first side 5a that is arranged in damping piston and the first movement restriction device 11
17iWith outer diameter d
17yBetween radially extend.Space 17 has a certain compressing area 17 ' with respect to a certain degree of depth of first piston surface 5a.The inner diameter d in space 17
17iDiameter d greater than piston rod/piston rod extending portion
4
The inner diameter d in space
17iAnd the surface of the first side 5a of the damping piston that causes between the piston rod can be decided to be the first damping piston surface 5a '.The outer diameter d in space
17yThe zone of the first damping piston surface 5a ' in the outside can be decided to be the second damping piston surface 5a ".
According to the design of damping piston 5, constricted zone 17 ' also can one the tunnel extends to the second damping piston surface 5a " outer diameter.Therefore, the outer diameter d in space
17yOutwards mobile, and the first flow limiter 11 that is in operating position is against the second damping piston surface 5a " minimum outer surface.When flow limiter was opened, resisting medium was corresponding to damping piston surface 5a " adhesion characteristics be minimized.
The first damping piston surface 5a ' is with respect to the surperficial 5a of the second damping piston " be offset so that the space with respect to the depth z 1 of the surperficial 5a ' of the first damping piston than the space with respect to the surperficial 5a of the second damping piston " depth z 2 shallow.
Space 17 is around piston rod 4, and the first pipe 9 leads to this space.Therefore, the resisting medium that flows by these first pipes 9 can spread in the space 17, in this space 17, resisting medium is contributed the increase to power, and this produces on the first flow limiter 11 this energetically so that the first flow limiter 11 begins to open in a certain value.When damping piston 5 when its restriction site moves and is arranged in the restricted quarter 6, additional reaction force F2 is in fact constant basically in whole stroke.This is because the restriction between damping piston 5 and the first flow limiter 11 reduces highly rapidly along with improving.
The outer diameter d in space 17
17yBe so large, so that the slight increase of the raising of the first flow limiter 11 height allows relatively large resisting medium to flow through damping piston 5, see Fig. 3 c.Therefore, resisting medium flows and is determined by axially extended opened areas.Opened areas is the envelope zone (enveloping area) of opening, and thereby as the outer diameter d in space
17yChange with the function that improves height s.
Fig. 3 c represents also when the first flow limiter 11 is exposed to enough reaction force F2 how the first flow limiter 11 is out of shape.When piston rod 4 moves by a certain minimum speed with the direction R1 towards restriction site at least with respect to damped cylinder and damping piston 5 when reaching the restricted quarter 6, produce completely breaking force F2.Because the inside 11a of the process that flows damping piston 5, the first flow limiters presses to the first damping piston surface 5a ', and the outside 11b of the first flow limiter presses to the second damping piston surface 5a ".When the first flow limiter is opened, its outside 11b thereby " discharge a certain distance, but the inside 11a of the first flow limiter continues to press to the first damping piston surface 5a ' from the second damping piston surface 5a.
Fig. 4 a-4c only represents to have the damping piston 5 of the mouth of pipe and the flowing space.Damping piston 5 on the direction of its second surface 5b at its outer diameter d
5yThe place has cuts sth. askew, and centers in the restricted quarter 6 thereby be convenient to damping piston 5.Fig. 4 a represents second surface 5b and strong point 12a, the 12b of the second flow limiter 12 and the view of 12c of damping piston.Fig. 4 c represents the view of the first surface 5a of damping piston, the outer diameter d of representation space 17
17yWith inner diameter d
17iThe first damping piston zone 5a ' is at the inner diameter d of damping piston
5iInner diameter d with the space
17iBetween extend and the second damping piston zone 5a " outer diameter d in the space
17yOuter diameter d with damping piston
5yAnd between extend.
Changing again of vibration damper, uses two damping pistons 5, see Fig. 5, one at the either side of main piston 3 in order to produce the reaction force that adds in the restriction site of two stroke direction R1, R2.Damping piston 5 is designed in the same manner described above.
The invention is not restricted to illustrated embodiment, for example by pressurization in abutting connection with main piston or a space directly sharing in abutting connection with two dampening chamber of pressurized reservoir, the both sides of main piston all pressurized vibration damper also are feasible.In addition, flow limiter can be any type of mitre velve, and thereby needs not be the pad valve.The present invention also can be changed under the condition that does not deviate from appended Patent right requirement or idea of the present invention.
Claims (51)
1. a traffic tool vibration damper (1), for generation of additional reaction force, described reaction force reacts on the parts (4 of relative to each other mobile described vibration damper, 2) movement direction in the movement between or the restriction site of stroke, wherein, described vibration damper comprises in fact the damped cylinder that is filled with resisting medium (2) of hydraulic pressure, described damped cylinder (2) is divided into two (C1 of dampening chamber by main piston (3), C2), described main piston (3) is axially removable and be connected in piston rod (4) with respect to described damped cylinder (2), and wherein, first end (4a) in described piston rod (4) is located, center on every side at damping piston holder (13), also be furnished with at least damping piston (5), first side (5a) of described damping piston (5) is towards described main piston (3) and comprise one or more the first siphunculus (9) and the second siphunculus (10), wherein, the at least the first siphunculus (9) in these pipes is limited with the flow direction on described first side (5a) of described damping piston by the first flow limiter (11), described the first flow limiter (11) produces flow by the restriction of the resisting medium of the first siphunculus (9), and wherein, described damping piston (5) has the outside piston diameter d less than the outer diameter of described main piston (3)
5y, and described damping piston (5) is used in the restricted quarter (6) sliding, the described restricted quarter (6) be positioned at and hydraulic link in described damped cylinder (2), but have inner diameter d less than described damped cylinder
2iInner diameter d
6iSo that the braking of damping movement produces at the stroke place of a certain magnitude, it is characterized in that, when described damping piston (5) when its restriction site moves and be arranged in the described restricted quarter (6), the described reaction force that reacts on described movement direction is in fact constant in whole stroke, and be that the resisting medium stream of minimum flow is by the described inner diameter d of described damping piston (5) and the described restricted quarter (6)
6iBetween, the described resisting medium stream that acts on described the first flow limiter (11) this moment works in space (17), described space (17) is arranged between described first side (5a) away from described movement direction of described the first flow limiter (11) and described damping piston (5), and described space (17) have a large outer diameter scope d
17y, when opening flow path by described the first siphunculus (9) with the pressure reduction on the described damping piston of box lunch (5), the restriction of described resisting medium stream is along with the mobile minimum level ground change that increases.
2. vibration damper according to claim 1 (1), it is characterized in that, when opening by the described flow path of described the first siphunculus (9), described the first flow limiter (11) rises a certain raising highly from described damping piston (5), in order to produce opened areas between described first side (5a) away from described movement direction of described the first flow limiter (11) and described damping piston (5), described opened areas is determined the restriction of described resisting medium stream.
3. vibration damper according to claim 2 (1) is characterized in that, described damping piston (5) is designed to respect to described piston rod (4) with axially and move radially, so that at the outer diameter d of described damping piston
5yWith inner diameter d
6iThe internal surface of the described restricted quarter (6) between do not produce under the condition of big difference, the modulation of the described restricted quarter is possible.
4. described vibration damper (1) one of according to claim 1-3, it is characterized in that, externally damping piston surface (tension between 5a ") and the internally-damped piston (5a '); (5a ") and described internally-damped piston (5a ') relative to each other depart from described out-damping piston face, react on described movement in order to produce large reaction force (F2) of described the first flow limiter (11).
5. vibration damper according to claim 4 (1), it is characterized in that, when the pressure against described damping piston (5) becomes large so that first-class moving limiter (11) is in maximum tension and presses to described internally-damped piston face (5a ') and described out-damping piston face (during 5a "), needs to be used for opening the described reaction force (F2) of developing fully of described the first flow limiter (11).
6. described vibration damper (1) one of according to claim 1-3, it is characterized in that, this vibration damper (1) is designed at two stroke direction (R1, R2) produce additional reaction force in the restriction site, and be that damping piston (5) is positioned at each dampening chamber (C1, C2), described each dampening chamber (C1, C2) all has the first side (5a) towards described main piston (3).
7. vibration damper according to claim 4 (1), it is characterized in that, this vibration damper (1) is designed at two stroke direction (R1, R2) produce additional reaction force in the restriction site, and be that damping piston (5) is positioned at each dampening chamber (C1, C2), described each dampening chamber (C1, C2) all has the first side (5a) towards described main piston (3).
8. vibration damper according to claim 5 (1), it is characterized in that, this vibration damper (1) is designed at two stroke direction (R1, R2) produce additional reaction force in the restriction site, and be that damping piston (5) is positioned at each dampening chamber (C1, C2), described each dampening chamber (C1, C2) all has the first side (5a) towards described main piston (3).
9. vibration damper according to claim 1 (1) is characterized in that, described two dampening chamber (C1, C2) are respectively pressing chamber and reversion chamber.
10. a traffic tool vibration damper (1), described traffic tool vibration damper (1) comprises in fact the damped cylinder (2) that hydraulic pressure is filled with medium, described damped cylinder (2) is divided into two (C1 of dampening chamber by main piston (3), C2), described main piston (3) is axially removable and be connected in piston rod (4) with respect to described damped cylinder (2), wherein, first end (4a) in described piston rod (4) is located, damping piston holder (13) at described piston rod (4) centers on every side, also be furnished with at least damping piston (5), first side (5a) of described damping piston (5) is towards described main piston (3) and comprise one or more the first siphunculus (9) and the second siphunculus (10), wherein, the at least the first siphunculus (9) in these pipes is limited with the flow direction on described first side (5a) of described damping piston by the first flow limiter (11), and wherein, described damping piston (5) has the outside piston diameter d less than the outer diameter of described main piston (3)
5y, and described damping piston (5) be used for be arranged in and hydraulic link in the slip of the restricted quarter (6) of described damped cylinder (2), but have inner diameter d less than described damped cylinder
2iInner diameter d
6iIt is characterized in that, the first siphunculus (9) in the damping piston siphunculus leads to space (17), and described space (17) are positioned between described first side (5a) and described the first flow limiter (11) of described damping piston, at inner diameter scope d
17iWith outer diameter scope d
17yBetween, described space (17) have constricted zone (17 '), and described constricted zone (17 ') is greater than zone or the overall area of described the first siphunculus (9).
11. vibration damper according to claim 10 (1), it is characterized in that, the pressure that acts on the described constricted zone (17 ') improves a distance with described the first flow limiter, and described distance is basically as the outer diameter scope d of described space (17)
17yFunction change.
12. according to claim 10 or 11 described vibration dampers (1), it is characterized in that, described damping piston (5) is designed to have the radial internal clearance x around described damping piston holder (13), but at the described inner diameter d of described damping piston (5) and the described restricted quarter (6)
6iBetween have minimum play.
13. vibration damper according to claim 10 (1), it is characterized in that, described damping piston (5) can be axially mobile with respect to described damping piston holder (13), and be, axial internal clearance by be arranged in the described damping piston holder (13) or on two position limitation spares (14,15) produce and restriction described position limitation spare (14,15) on each side of described damping piston (5) each.
14. vibration damper according to claim 11 (1), it is characterized in that, described damping piston (5) can be axially mobile with respect to described damping piston holder (13), and be, axial internal clearance by be arranged in the described damping piston holder (13) or on two position limitation spares (14,15) produce and restriction described position limitation spare (14,15) on each side of described damping piston (5) each.
15. vibration damper according to claim 12 (1), it is characterized in that, described damping piston (5) can be axially mobile with respect to described damping piston holder (13), and be, axial internal clearance by be arranged in the described damping piston holder (13) or on two position limitation spares (14,15) produce and restriction described position limitation spare (14,15) on each side of described damping piston (5) each.
16. according to claim 13 or 14 described vibration dampers (1), it is characterized in that described damping piston (5) produces with to resistive drag force axial direction mobile.
17. vibration damper according to claim 15 (1) is characterized in that, described damping piston (5) produces with to resistive drag force axial direction mobile.
18. vibration damper according to claim 16 (1), it is characterized in that, described damping piston (5) produces by the elastic device (18) that is arranged between any in described damping piston (5) and the described position limitation spare (14,15) at the moving resistance of axial direction.
19. vibration damper according to claim 17 (1), it is characterized in that, described damping piston (5) produces by the elastic device (18) that is arranged between any in described damping piston (5) and the described position limitation spare (14,15) at the moving resistance of axial direction.
20. vibration damper according to claim 16 (1) is characterized in that, described damping piston (5) is produced in the tension by described the first flow limiter (11) of the moving resistance of the movement of axial direction.
21. vibration damper according to claim 17 (1) is characterized in that, described damping piston (5) is produced in the tension by described the first flow limiter (11) of the moving resistance of the movement of axial direction.
22. vibration damper according to claim 18 (1) is characterized in that, described damping piston (5) is produced in the tension by described the first flow limiter (11) of the moving resistance of the movement of axial direction.
23. vibration damper according to claim 19 (1) is characterized in that, described damping piston (5) is produced in the tension by described the first flow limiter (11) of the moving resistance of the movement of axial direction.
24. vibration damper according to claim 20 (1), it is characterized in that, the tension of described the first flow limiter (11) is because following former thereby produce: described the first flow limiter that is in the close position presses to the first damping piston surface (5a ') on described first side (5a) of described damping piston and the second damping piston surface, and (5a "), described the first damping piston surface (5a ') and described the second damping piston are surperficial, and (5a ") relative to each other departs from.
25. vibration damper according to claim 21 (1), it is characterized in that, the tension of described the first flow limiter (11) is because following former thereby produce: described the first flow limiter that is in the close position presses to the first damping piston surface (5a ') on described first side (5a) of described damping piston and the second damping piston surface, and (5a "), described the first damping piston surface (5a ') and described the second damping piston are surperficial, and (5a ") relative to each other departs from.
26. vibration damper according to claim 22 (1), it is characterized in that, the tension of described the first flow limiter (11) is because following former thereby produce: described the first flow limiter that is in the close position presses to the first damping piston surface (5a ') on described first side (5a) of described damping piston and the second damping piston surface, and (5a "), described the first damping piston surface (5a ') and described the second damping piston are surperficial, and (5a ") relative to each other departs from.
27. vibration damper according to claim 23 (1), it is characterized in that, the tension of described the first flow limiter (11) is because following former thereby produce: described the first flow limiter that is in the close position presses to the first damping piston surface (5a ') on described first side (5a) of described damping piston and the second damping piston surface, and (5a "), described the first damping piston surface (5a ') and described the second damping piston are surperficial, and (5a ") relative to each other departs from.
28. vibration damper according to claim 24 (1) is characterized in that, described the first damping piston surface (5a ') is arranged in the inner diameter scope d in described space
17iIn, (5a ") is arranged in the outer diameter scope d in described space and described the second damping piston is surperficial
17yOutward.
29. vibration damper according to claim 25 (1) is characterized in that, described the first damping piston surface (5a ') is arranged in the inner diameter scope d in described space
17iIn, (5a ") is arranged in the outer diameter scope d in described space and described the second damping piston is surperficial
17yOutward.
30. vibration damper according to claim 26 (1) is characterized in that, described the first damping piston surface (5a ') is arranged in the inner diameter scope d in described space
17iIn, (5a ") is arranged in the outer diameter scope d in described space and described the second damping piston is surperficial
17yOutward.
31. vibration damper according to claim 27 (1) is characterized in that, described the first damping piston surface (5a ') is arranged in the inner diameter scope d in described space
17iIn, (5a ") is arranged in the outer diameter scope d in described space and described the second damping piston is surperficial
17yOutward.
32. according to claim 10-11 and each the described vibration damper (1) among the 13-14, it is characterized in that, two damping pistons (5) that are arranged on the piston rod (4) all have it towards first side (5a) of described main piston (3), in described two damping pistons (5), a damping piston is on the first side of described main piston (3), and another damping piston is on the second side of described main piston (3).
33. vibration damper according to claim 12 (1), it is characterized in that, two damping pistons (5) that are arranged on the piston rod (4) all have it towards first side (5a) of described main piston (3), in described two damping pistons (5), a damping piston is on the first side of described main piston (3), and another damping piston is on the second side of described main piston (3).
34. vibration damper according to claim 15 (1), it is characterized in that, two damping pistons (5) that are arranged on the piston rod (4) all have it towards first side (5a) of described main piston (3), in described two damping pistons (5), a damping piston is on the first side of described main piston (3), and another damping piston is on the second side of described main piston (3).
35. vibration damper according to claim 16 (1), it is characterized in that, two damping pistons (5) that are arranged on the piston rod (4) all have it towards first side (5a) of described main piston (3), in described two damping pistons (5), a damping piston is on the first side of described main piston (3), and another damping piston is on the second side of described main piston (3).
36. vibration damper according to claim 17 (1), it is characterized in that, two damping pistons (5) that are arranged on the piston rod (4) all have it towards first side (5a) of described main piston (3), in described two damping pistons (5), a damping piston is on the first side of described main piston (3), and another damping piston is on the second side of described main piston (3).
37. vibration damper according to claim 18 (1), it is characterized in that, two damping pistons (5) that are arranged on the piston rod (4) all have it towards first side (5a) of described main piston (3), in described two damping pistons (5), a damping piston is on the first side of described main piston (3), and another damping piston is on the second side of described main piston (3).
38. vibration damper according to claim 19 (1), it is characterized in that, two damping pistons (5) that are arranged on the piston rod (4) all have it towards first side (5a) of described main piston (3), in described two damping pistons (5), a damping piston is on the first side of described main piston (3), and another damping piston is on the second side of described main piston (3).
39. vibration damper according to claim 20 (1), it is characterized in that, two damping pistons (5) that are arranged on the piston rod (4) all have it towards first side (5a) of described main piston (3), in described two damping pistons (5), a damping piston is on the first side of described main piston (3), and another damping piston is on the second side of described main piston (3).
40. vibration damper according to claim 21 (1), it is characterized in that, two damping pistons (5) that are arranged on the piston rod (4) all have it towards first side (5a) of described main piston (3), in described two damping pistons (5), a damping piston is on the first side of described main piston (3), and another damping piston is on the second side of described main piston (3).
41. vibration damper according to claim 22 (1), it is characterized in that, two damping pistons (5) that are arranged on the piston rod (4) all have it towards first side (5a) of described main piston (3), in described two damping pistons (5), a damping piston is on the first side of described main piston (3), and another damping piston is on the second side of described main piston (3).
42. vibration damper according to claim 23 (1), it is characterized in that, two damping pistons (5) that are arranged on the piston rod (4) all have it towards first side (5a) of described main piston (3), in described two damping pistons (5), a damping piston is on the first side of described main piston (3), and another damping piston is on the second side of described main piston (3).
43. vibration damper according to claim 24 (1), it is characterized in that, two damping pistons (5) that are arranged on the piston rod (4) all have it towards first side (5a) of described main piston (3), in described two damping pistons (5), a damping piston is on the first side of described main piston (3), and another damping piston is on the second side of described main piston (3).
44. vibration damper according to claim 25 (1), it is characterized in that, two damping pistons (5) that are arranged on the piston rod (4) all have it towards first side (5a) of described main piston (3), in described two damping pistons (5), a damping piston is on the first side of described main piston (3), and another damping piston is on the second side of described main piston (3).
45. vibration damper according to claim 26 (1), it is characterized in that, two damping pistons (5) that are arranged on the piston rod (4) all have it towards first side (5a) of described main piston (3), in described two damping pistons (5), a damping piston is on the first side of described main piston (3), and another damping piston is on the second side of described main piston (3).
46. vibration damper according to claim 27 (1), it is characterized in that, two damping pistons (5) that are arranged on the piston rod (4) all have it towards first side (5a) of described main piston (3), in described two damping pistons (5), a damping piston is on the first side of described main piston (3), and another damping piston is on the second side of described main piston (3).
47. vibration damper according to claim 28 (1), it is characterized in that, two damping pistons (5) that are arranged on the piston rod (4) all have it towards first side (5a) of described main piston (3), in described two damping pistons (5), a damping piston is on the first side of described main piston (3), and another damping piston is on the second side of described main piston (3).
48. vibration damper according to claim 29 (1), it is characterized in that, two damping pistons (5) that are arranged on the piston rod (4) all have it towards first side (5a) of described main piston (3), in described two damping pistons (5), a damping piston is on the first side of described main piston (3), and another damping piston is on the second side of described main piston (3).
49. vibration damper according to claim 30 (1), it is characterized in that, two damping pistons (5) that are arranged on the piston rod (4) all have it towards first side (5a) of described main piston (3), in described two damping pistons (5), a damping piston is on the first side of described main piston (3), and another damping piston is on the second side of described main piston (3).
50. vibration damper according to claim 31 (1), it is characterized in that, two damping pistons (5) that are arranged on the piston rod (4) all have it towards first side (5a) of described main piston (3), in described two damping pistons (5), a damping piston is on the first side of described main piston (3), and another damping piston is on the second side of described main piston (3).
51. vibration damper according to claim 10 (1) is characterized in that, described two dampening chamber (C1, C2) are respectively pressing chamber and reversion chamber.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| SE0702798-0 | 2007-12-14 | ||
| SE0702798A SE531501C2 (en) | 2007-12-14 | 2007-12-14 | Shock absorbers with increasing damping force |
| PCT/SE2008/051431 WO2009078791A1 (en) | 2007-12-14 | 2008-12-10 | Shock absorber with increasing damping force |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101896732A CN101896732A (en) | 2010-11-24 |
| CN101896732B true CN101896732B (en) | 2013-01-02 |
Family
ID=40568152
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2008801209286A Active CN101896732B (en) | 2007-12-14 | 2008-12-10 | Shock absorber with increasing damping force |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US8955654B2 (en) |
| EP (1) | EP2232095B1 (en) |
| JP (2) | JP2011506874A (en) |
| CN (1) | CN101896732B (en) |
| SE (1) | SE531501C2 (en) |
| WO (1) | WO2009078791A1 (en) |
Families Citing this family (23)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5542390B2 (en) * | 2009-08-24 | 2014-07-09 | 不二ラテックス株式会社 | Liquid damper device |
| US8991840B2 (en) * | 2013-03-14 | 2015-03-31 | Oshkosh Defense, Llc | Load dependent damper for a vehicle suspension system |
| EP2792901B1 (en) | 2013-04-16 | 2016-05-18 | Öhlins Racing Ab | Valve arrangement |
| CN103953676B (en) | 2014-05-14 | 2015-10-21 | 北京京西重工有限公司 | There is hydraulic damper and the manufacture method thereof of hydraulic pressure stop configurations |
| CN107429774B (en) | 2015-02-06 | 2019-09-27 | 天纳克汽车营运公司 | Secondary damper assembly for damper |
| RU2015111360A (en) | 2015-03-30 | 2016-10-20 | Общество С Ограниченной Ответственностью "Яндекс" | Method (options) and system (options) for processing a search query |
| US10107352B2 (en) | 2016-04-29 | 2018-10-23 | Beijingwest Industries Co., Ltd. | Hydraulic damper with a hydraulic stop arrangement |
| DE102016210789B4 (en) * | 2016-06-16 | 2020-08-06 | Zf Friedrichshafen Ag | Damping valve for a vibration damper |
| US10239376B2 (en) * | 2016-09-22 | 2019-03-26 | Beijingwest Industries Co., Ltd. | Hydraulic damper with an x-flow piston assembly |
| EP3604103A4 (en) * | 2017-03-22 | 2020-03-18 | Honda Motor Co., Ltd. | Steering damper |
| US10883458B2 (en) | 2017-07-03 | 2021-01-05 | Vitesco Technologies USA, LLC. | Asymmetric spring valve disk |
| USD869259S1 (en) | 2017-08-28 | 2019-12-10 | Qa1 Precision Products, Inc. | Valve component |
| US11105390B2 (en) | 2017-08-28 | 2021-08-31 | Qa1 Precision Products, Inc. | Shock absorber with dry valving |
| USD872837S1 (en) | 2017-08-28 | 2020-01-14 | Qa1 Precision Products, Inc. | Bleed needle |
| US11085502B2 (en) | 2017-08-28 | 2021-08-10 | Qa1 Precision Products, Inc. | Bleed needle for a hydraulic system |
| USD866408S1 (en) | 2017-08-28 | 2019-11-12 | Qa1 Precision Products, Inc. | Shock absorber |
| DE102018201297B4 (en) * | 2018-01-29 | 2022-07-07 | Bayerische Motoren Werke Aktiengesellschaft | Vibration damper for a vehicle |
| US11448282B2 (en) | 2018-06-20 | 2022-09-20 | N10Z Performance Shocks LLC | Shock absorber assembly |
| US11434968B2 (en) * | 2019-02-25 | 2022-09-06 | Mark Brendan Newhan | Vehicle shock absorber |
| US11279194B2 (en) * | 2020-04-02 | 2022-03-22 | Thyssenkrupp Bilstein Of America Inc. | Damper with reservoir |
| CA3139485A1 (en) * | 2020-11-26 | 2022-05-26 | Bombardier Recreational Product Inc. | Shock absorber for a vehicle |
| CN115071357B (en) * | 2022-06-30 | 2024-08-13 | 中国第一汽车股份有限公司 | Vehicle suspension control system, method, vehicle and storage medium |
| CN117150953B (en) * | 2023-08-21 | 2024-06-14 | 北京建筑大学 | Method and system for predicting damping force of double-order viscous damper |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB998742A (en) * | 1962-03-29 | 1965-07-21 | Automobilove Zd Y Letnany | Improvements in or relating to telescopic shock absorbers |
| US4106596A (en) * | 1975-11-17 | 1978-08-15 | Firma August Bilstein | Hydropneumatic single tube shock absorber, in particular steering shock absorber |
| US5810128A (en) * | 1995-05-18 | 1998-09-22 | Yamaha Hatsudoki Kabushiki Kaisha | Shock absorber |
| US6776269B1 (en) * | 2003-06-18 | 2004-08-17 | Tenneco Automotive Operating Company, Inc. | Twin piston shock absorber |
| CN2797766Y (en) * | 2005-05-31 | 2006-07-19 | 嘉兴市嘉力达汽车部件有限公司 | Air filled double piston type shock absorber |
Family Cites Families (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3175645A (en) * | 1962-09-13 | 1965-03-30 | Stabilus Ind Handels Gmbh | Shock absorber with primary and secondary damping chambers |
| GB1132038A (en) * | 1966-03-17 | 1968-10-30 | Woodhead Mfg Company Ltd | Vibration dampers |
| US4624347A (en) * | 1984-01-23 | 1986-11-25 | Ford Motor Company | Piston assembly for shock absorber |
| US4653339A (en) * | 1984-12-06 | 1987-03-31 | Atsugi Motor Parts Co., Ltd. | Rack-and-pinion steering gear for a vehicle |
| US5332069A (en) * | 1989-08-31 | 1994-07-26 | Kayaba Kogyo Kabushiki Kaisha | Shock absorber |
| JPH03140644A (en) * | 1989-10-21 | 1991-06-14 | Nhk Spring Co Ltd | Damping force generator |
| ES2115429B1 (en) * | 1993-05-10 | 1999-02-16 | Fichtel & Sachs Ag | VALVE FOR A HYDRAULIC TELESCOPIC VIBRATION DAMPER. |
| JPH0960680A (en) * | 1995-08-19 | 1997-03-04 | Tokico Ltd | Hydraulic shock absorber |
| SE515321C2 (en) * | 1998-12-02 | 2001-07-16 | Oehlins Racing Ab | Shock absorber with cylinder comprising a piston rod with at least two pistons |
| JP2000283117A (en) * | 1999-03-29 | 2000-10-13 | Hitachi Constr Mach Co Ltd | Hydraulic cylinder |
| CA2403419A1 (en) * | 2001-09-14 | 2003-03-14 | Bombardier Inc. | Shock absorber with a floating piston |
| DE10163217B4 (en) * | 2001-12-21 | 2014-10-09 | Volkswagen Ag | damper valve |
| US7441640B2 (en) * | 2003-10-08 | 2008-10-28 | Peter Russell | Shock absorber apparatus |
| DE10351357B3 (en) * | 2003-11-04 | 2005-02-24 | Zf Friedrichshafen Ag | Fluid resistance valve for use in vibration damper has valve flaps pushed down onto plate with holes or parallel against Belleville washer to allow flow of fluid through holes |
| KR101218839B1 (en) * | 2010-09-07 | 2013-01-07 | 주식회사 만도 | Sock absorber |
-
2007
- 2007-12-14 SE SE0702798A patent/SE531501C2/en unknown
-
2008
- 2008-12-10 JP JP2010537897A patent/JP2011506874A/en active Pending
- 2008-12-10 CN CN2008801209286A patent/CN101896732B/en active Active
- 2008-12-10 US US12/747,478 patent/US8955654B2/en active Active
- 2008-12-10 WO PCT/SE2008/051431 patent/WO2009078791A1/en active Application Filing
- 2008-12-10 EP EP08862162.8A patent/EP2232095B1/en active Active
-
2015
- 2015-02-02 JP JP2015018658A patent/JP6084643B2/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB998742A (en) * | 1962-03-29 | 1965-07-21 | Automobilove Zd Y Letnany | Improvements in or relating to telescopic shock absorbers |
| US4106596A (en) * | 1975-11-17 | 1978-08-15 | Firma August Bilstein | Hydropneumatic single tube shock absorber, in particular steering shock absorber |
| US5810128A (en) * | 1995-05-18 | 1998-09-22 | Yamaha Hatsudoki Kabushiki Kaisha | Shock absorber |
| US6776269B1 (en) * | 2003-06-18 | 2004-08-17 | Tenneco Automotive Operating Company, Inc. | Twin piston shock absorber |
| CN2797766Y (en) * | 2005-05-31 | 2006-07-19 | 嘉兴市嘉力达汽车部件有限公司 | Air filled double piston type shock absorber |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2232095A4 (en) | 2017-08-02 |
| EP2232095B1 (en) | 2021-04-07 |
| JP6084643B2 (en) | 2017-02-22 |
| US20110017558A1 (en) | 2011-01-27 |
| US8955654B2 (en) | 2015-02-17 |
| SE0702798L (en) | 2009-04-28 |
| JP2015121326A (en) | 2015-07-02 |
| EP2232095A1 (en) | 2010-09-29 |
| WO2009078791A1 (en) | 2009-06-25 |
| JP2011506874A (en) | 2011-03-03 |
| CN101896732A (en) | 2010-11-24 |
| SE531501C2 (en) | 2009-04-28 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101896732B (en) | Shock absorber with increasing damping force | |
| US9091319B2 (en) | Shock absorber with hydraulic flow ducts | |
| KR101208653B1 (en) | - pneumatic spring shock absorber unit | |
| CN1965174A (en) | Electronically controlled frequency dependent damping | |
| KR20060055539A (en) | Shock absorber assembly | |
| KR101518097B1 (en) | Hydropneumatic suspension unit | |
| CN107614924B (en) | Shock absorber | |
| JP4898613B2 (en) | Shock absorber | |
| EP2126403B1 (en) | Method for adjusting damping characteristics in a shock absorber | |
| CZ22828U1 (en) | Gas-filled spring device with damping | |
| CN210769980U (en) | Buffer, shock absorber and vehicle | |
| US20220412425A1 (en) | Vehicle Shock Absorber | |
| KR20210031077A (en) | Shock absorber for vehicle | |
| GB2547479A (en) | Suspension assembly for a vehicle | |
| CN117469337A (en) | Frequency-sensitive shock absorber | |
| US20060163017A1 (en) | Hollow rod monotube shock absorber | |
| JPH02283928A (en) | Displacement sensitive type hydraulic damper | |
| JP7422941B2 (en) | buffer | |
| KR100331644B1 (en) | Shock absorber | |
| WO2024019682A1 (en) | A piston assembly including a spring for secondary damping | |
| KR20140135070A (en) | shock absorber | |
| JP3991661B2 (en) | shock absorber | |
| KR20240008777A (en) | Body valve assembly and frequency sensitive type shock absorber with the same | |
| KR20240008778A (en) | Piston valve assembly and frequency sensitive type shock absorber with the same | |
| JP2020020373A (en) | Base-isolation damper |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant |